Centrifugal governor for controlling the rpm of injection type internal combustion engines

ABSTRACT

A centrifugal governor for controlling the rpm of an injection type internal combustion engine having a fuel injection pump is described which governor has a housing and a regulator member being displaceable as a function of the rpm, and the regulating movements of which member are transmitted, by means of a twoarmed cam lever having lever arms which are adjustable dependent upon the position given an externally turnable operating lever, to fuel delivery control means associated with the fuel injection pump, wherein the fuel delivery control means, upon completing a first part of its movement against the force of a first control spring, acts on a force-transmitting lever which is biassed by at least one second control spring; the force-transmitting lever bears an adjusting screw for setting the first control spring to a low rpm, and is adapted for swivelling about an axis which is stationary in the governor housing, and wherein the neutral position of the force-transmitting lever is determined by a stop fixed in the housing. This governor is improved by providing therein (A) A BEARING LEVER ADJUSTABLE FOR SETTING A MAXIMUM RPM AND BEARING A SPRING SEAT FOR THE AFORESAID SECOND CONTROL SPRING, (B) A SECOND ADJUSTING SCREW FOR THE BEARING LEVER, AND (C) AND ADJUSTING ELEMENT FOR LIMITING THE FIRST PART OF THE MOVEMENT OF THE REGULATOR MEMBER, THE BEARING LEVER, SECOND ADJUSTING SCREW AND ADJUSTING ELEMENT BEING IN ENGAGEMENT WITH THE FORCE-TRANSMITTING LEVER.

United States Patent [191 Bechstein et al.

11 3,830,211 [451 Aug. 20, 1974 CENTRIFUGAL GOVERNOR FOR CONTROLLING THE RPM OF INJECTION TYPE INTERNAL COMBUSTION ENGINES [75] Inventors: Herbert Bechstein, Esslingen;

Hans-Jurgen Jaenke, Ditzingen; Rolf Muller, Stuttgart-Freiberg; Ernst Ritter, Stuttgart; Heinrich Staudt, Markgronigen-Talhausen, all of Germany [73] Assignee: Robert Bosch GmbH, Stuttgart,

Germany [22] Filed: May 21, 1973 [21] Appl. No.: 362,302

[30] Foreign Application Priority Data Primary ExaminerLaurence M. Goodridge Assistant Examiner-Cort Flint Attorney, Agent, or Firm-Edwin E. Greigg 57 ABSTRACT A centrifugal governor for controlling the rpm of an injection type internal combustion engine having a fuel injection pump is described which governor has a housing and a regulator member being displaceable as a function of the rpm, and the regulating movements of which member are transmitted, by means of a twoarmed cam lever having lever arms which are adjustable dependent upon the position given an externally tumable operating lever, to fuel delivery control means associated with the fuel injection pump, wherein the fuel delivery control means, upon completing a first part of its movement against the force of a first control spring, acts on a force-transmitting lever which is biassed by at least one second control spring; the force-transmitting lever bears an adjusting screw for setting the first control spring to a low rpm, and is adapted for swivelling about an axis which is stationary in the governor housing, and wherein the neutral position of the force-transmitting lever is determined by a stop fixed in the housing. This governor is improved by providing therein (a) a bearing lever adjustable for setting a maximum rpm and bearing a spring seat for the aforesaid second control spring,

(b) a second adjusting screw for the bearing lever, and

(c) and adjusting element for limiting the first part of the movement of the regulatormember, the bearing lever, second adjusting screw and adjusting element being in engagement with the force-transmitting lever.

18 Claims, 3 Drawing Figures CENTRIFUGAL GOVERNOR FOR CONTROLLING THE RPM OF INJECTION TYPE INTERNAL COMBUSTION ENGINES BACKGROUND OF THE INVENTION The invention relates to a centrifugal governor for controlling the rpm of injection type internal combustion engines having a fuel injection pump, which governor has a housing and a regulator member being displaceable as a function of the rpm, and the regulating movements of which member are transmitted, by means of a two-armed cam lever having lever arms which are adjustable dependent upon the position given an externally turnable operating lever, to fuel delivery control means associated with the fuel injection pump, wherein the fuel delivery control means, upon completing a first part of its movements against the force of a first control spring, acts on a forcetransmitting lever which is biassed by at least one second control spring, and the force-transmitting lever bears an adjusting screw for setting the first control spring to a low rpm, and is adapted for swivelling about an axis which is stationary in the governor housing, and wherein the neutral position of the force-transmitting lever is determined by a stop fixed in the housing.

Various rpm-regulating centrifugal governors of the above outlined structure have been known, which have been used as no-load governors and as final speed governors, or which operate as adjustable rpm-regulating governors with insertion of a spring-type storage device among the connecting elements between the regulator member and the fuel delivery control member. Due to the use of the connecting linkage and the forcetransmitting lever, these known governors have an advantage over other rpm-regulating governors of similar construction, in that the adjustment of the amount of fuel to be delivered, and/or the adjustment of the rpms to be regulated is simple and without any disturbing counteracting forces while the operating lever is actuated. A disadvantage of the known governors however, resides in that the adjustment of the rpms to be regulated and the adjustment of the working ranges of the governor, i.e., the exact coordination of the respective positions of the fuel delivery control member in relation to the positions of the regulator member, is intricate, as some individual adjustment steps will influence, at least in part, others. Thus, in the case of a known governor of the aboveoutlined structure for instance, the adjustment of the full-load position of the regulator sleeve will cause changes in the initial tension of the no-load control spring as well as that of the fullload control spring.

OBJECTS AND GENERAL DESCRIPTION OF THE INVENTION It is, therefore, an object of this invention to provide the second control spring, as well as an associated adjusting screw and an adjusting member for limiting the first part of the movement of the regulator member.

A particularly advantageous feature of the rpmregulating governor according to the invention is provided by the fact that the force-transmitting lever, in its 7 neutral position, is disposed at least approximately perpendicular to the axis of the regulating member, and that the adjusting screw of the bearing lever, the adjusting member and the adjusting screw for the first control spring are screwed into the force-transmitting lever parallel in relation to one another and at least approximately parallel to the axis of the regulator member, and that they are secured in their position. This at least approximately horizontal arrangement of all adjusting elements is especially advantageous, since it allows an adjustment of the governor with access only from the front end thereof. A further advantage resides in that this arrangement facilitates the use of an automated adjusting device.

Of further advantage is the feature, whereby a stop screw isfitted into the governor housing in a position at least approximately parallel to the adjusting screws and to the adjusting member, which stop screw serves as a stop for the force-transmitting lever. This stop screw also could be adjusted with advantage by means of an automated setting device.

In a further advantageous embodiment of the inven' tion, the second control spring is devised as a tension spring which is arranged at least approximately in parallel to the force-transmitting lever, and the one end of which is connected to a bearing bolt which is rotatably mounted in the governor housing in parallel to the axis of the regulator member, and rotary displacement of which changes the effective direction of the second control spring and thereby causes an adjustment in the proportional range of the governor. As a result of this design and arrangement of the second control spring and of the bearing bolt, an adjustment of the proportional range can also be effected from the front face of the governor.

An embodiment of especially simple design is obtained, when the second spring support consists of a helicoidal groove of semi-circular profile machined into the bearing bolt.

In a preferred embodiment of the governor according to the invention, the force-transmitting lever features an essentially U- or H-shaped cross-section, and between its two parallel legs directed towards the injection pump there is mounted a bearing pin for the bearing lever. It is a particularly advantageous feature that the two legs contain a guide groove each for the guides protruding on the sides of the regulator member, which feature results in a simple and low-friction guidance of the regulator member.

As a further advantageous feature, the first control spring is preferably a leaf spring, and between the two aforesaid legs of the force-transmitting lever, there is provided a fixed abutment for the leaf spring; furthermore, the said fixed abutment for the leaf spring preferably comprises a recess in each one of the two legs; the leaf spring has two laterally projecting parts at one end which engage these recesses, and the leaf spring is supported at its other end by the guide pins of the regulator member, and the adjusting screw associated therewith is secured in its position by means of a screw connection in the cross-piece of the U or H-section of the force-transmitting lever intermediate both ends of the leaf spring. The arrangement of the first control spring serving as a no-load control spring, and of the adjusting screw associated therewith and with the forcetransmitting lever offers the advantage of having the influence of the first control spring upon the adjusting range of the second control spring eliminated.

An especially effective and space-saving embodiment is obtained by arranging at the force-transmitting lever an additional no-load spring, besides the two abovementioned control springs, which no-load spring is at least effective on part of the first portion of the displacement of the regulator member, and whose range of action is adjustable by means of an adjusting screw which is screwed into the force-transmitting lever and is secured in its position; furthermore, similar to the first control spring acting as a no-load control spring, the additional no-load spring is also designed as a leaf spring, which acts upon the regulator member by way of the first control spring; and still further, in addition a bi-metal spring is supported on the force-transmitting lever and acts upon the regulator member by way of the control spring. The no-load regulating range and the idling of the motor during warm-up can be adjusted by means of the additional no-load spring and the bimetal spring in a particularly simple manner without disturbing other regulating functions.

The invention will be better understood and further objects and advantages will become apparent from the ensuing detailed specification of a preferred but merely exemplary embodiment taken in conjunction with the drawings.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 represents a longitudinal sectional view of the embodiment taken in a plane along line II in FIG. 2;

FIG. 2 is a cross-sectional view of the same embodiment taken along line IIll in FIG. 1; and

FIG. 3 is a longitudinal sectional view taken along line III-III in FIG. 2.

DETAILED DESCRIPTION OF THE EMBODIMENT To the drive shaft of a fuel injection pump (not shown) for injection type internal combustion engines there is secured a face plate 11 on which there are pivotally mounted centrifugal fly weights 12. The arms 13 of the fly weights 12 engage the frontal face of a thrust collar 14 which is mounted on a stub of adaptor sleeve 15 serving as a regulator member, and which transmits the displacing forces of the centrifugal fly weights 12 by way of a thrust bearing 16 to the adaptor sleeve 15. The adaptor sleeve 15 is supported at its one end on a cylindrical stub 17 of the drive shaft 10, while its opposite end, away from the drive shaft, is fitted with laterally protruding guide pins 18, which are guided each in guide grooves 19 of a force-transmitting lever 21 (see also FIG. 3).

The force-transmitting lever 21 is a two-armed lever, which is pivotally secured against a pivot pin 38 fixed in the governor housing 37 and whose non-operational position as illustrated is determined by an abutment 39 fixed in the housing, the latter abutment being formed by the front end of a stop screw 41 which is screwed self-locking in the governor housing 37.

The force-transmitting lever 21 is of essentially U- or H-shaped cross-section, and its two legs 22 directed towards the injection pump contain the guide grooves 19 for the guide pins 18 of adaptor sleeve 15. An adjusting element 23 is screwed into the cross-piece 25 of the force-transmitting lever 21 at the same level as the axis of the drive shaft 10 and the adaptor sleeve 15, and is secured in position by means of a nut 24. The adjusting element 23 features an end plane 26, against which a convex surface 27 of the adaptor sleeve 15 abuts after having traversed a first part a of its path of travel.

While traversing the aforementioned first part a of its travel, the adaptor sleeve 15 acts upon a first control spring 28 which is designed as a leaf spring and which has its one end 29 supported on the force-transmitting lever 21, and the other end 31 of which exerts pressure on the guide pin 18 of the adaptor sleeve 15. The first end 29 of the leaf spring 28 has two laterally projecting parts 32, which are inserted into recesses 33 of the two legs 22 of the force-transmitting lever 21. These recesses 33 form a fixed abutment for the leaf spring 28. A bias exerted upon the adaptor sleeve 15 is produced by an adjusting screw 34 which is screwed into the crosspiece 25 of the force-transmitting lever 21 intermediate the two ends 29 and 31 of leaf spring 28, and which is secured in its setting by means of a nut 35.

The force-transmitting lever 21 can be swivelled counterclockwise around the pivot pin 38. This swivelling motion takes place whenever the force originating from the centrifugal fly weights 12 and transmitted by way of the adaptor sleeve 15 and the adjusting element 23 to the force-transmitting lever is larger than the resetting force emanating from a second control spring 42. This second control spring 42 is a tension spring which is arranged essentially perpendicular to the axis of the regulator member 15 in the governor and which is engaged at two abutments 43 and 44, of which the abutment 43 is located on an adjustable bearing lever 45 which serves for adjustment to the maximum rpm and which is connected with the force-transmitting lever 21 by means of a bearing pin 46 extending through the two legs 22 of the said lever 21. The bearing lever 45 is designed in the form of an angle lever and its illustrated position is determined by means of an adjusting screw 47 which serves to vary the bias of the second control spring 42. This bias determines in a known manner the maximum rpm to be regulated or limited by the governor.

The second abutment 44 of the control spring 42 is machined in the form of a helicoidal groove 48 of semicircular profile into a bearing bolt 49 which is arranged in the governor housing 37 in a position parallel to the axis of the regulator member 15, as well as parallel to the stop screw 41 and at least approximately parallel to the adjusting screws 34, and 47 and to the adjusting element 23. By means of a rotation of this bearing bolt 49, the proportional range of the governor may be adjusted, since by rotation of the bearing bolt 49, the point of suspension, i.e., the location of the second abutment 44, of the second control spring 42 is shifted horizontally in such a manner that the active direction of the control spring 42 is changed. Thereby, the effective rigidity of the spring 42 in relation to the force exerted on the force-transmitting lever 21. is changed in a known manner, which force counteracts, as a resetting force, the adjusting force of the adaptor sleeve 15.

In order that the bearing bolt 49 should not change its position during operation of the governor, a pressure screw 51 is screwed into the governor housing 37 in a known manner, slightly eccentrically of the central axis of bearing bolt 49 in the vicinity of one of the bearings of the said bolt 49 (see FIG. 3). The adaptor sleeve 15, opposing the resetting forces of the control springs 28 and 42, transmits its adjusting forces by way of an intermediate lever 53 and a cam lever 54, as well as a springtype accumulator 55, to the fuel delivery control rod 56 of the injection pump.

The linkage between the adaptor sleeve and the intermediate lever 53 is formed by a ball joint 57 (FIG. 1) consisting of a ball pin 58 and a bore 59 in a bearing arm 61 of the adaptor sleeve 15. The intermediate lever 53 is in the form of a U-shaped stirrup which is pivotally mounted in the governor housing 37 by means of two ball pivots 62 (see FIG. 2 for this detail) and which is linked by means of a pin 63 with the connecting linkage 54. The cam lever 54 is provided with a guide slot 64 (FIG. 3) which is engaged by a guide pin 65 of a steering lever 66 which pin is fixedly connected to a shaft 67 supported in governor housing 37. An operating lever 68 (FIG. 2) is secured to this shaft 67 outside the governor housing 37, whereby the shaft 67, together with the steering lever 66, can be swivelled and whereby, at the same time, together with the position of the control rod 56, the lever transmission ratio of the two-armed cam lever 54 will change. The two effective lever arms of the cam lever 54 are then constituted in a known manner, by the distances between the bolt 63 and the guide pin 65, on the one hand, and between the guide pin 65 and a connecting bolt 69 (FIG. 3), on the other hand; the latter bolt 69 connects the cam lever 54 and the spring-type accumulator 55 with one another. The shaft 67 (see FIG. 2 for this detail) which carries at one end, outside the governor housing 37, the operating lever 68, is provided at its other end with a stop lever 71 for limiting the pivoting angle of the operating lever and thereby also that of the steering lever 66 in conjunction with known stop means (not illustrated). Both levers 68 and 71 may, of course, also be arranged on the same side of the governor.

In order to prevent a stalling of the motor in particularly critical operating ranges, such as while abruptly closing the throttle, an additional no-load spring 73 is engaged at the force-transmitting lever 21 in addition to the first control spring 28 serving as no-load control spring (see F IG. 1 for this detail). This additional noload spring 73 is provided with a fixed spring seat in the form of a pin 74 which is mounted in the two legs 22 of the force-transmitting lever 21, and its active path b is adjustable by means of an adjusting screw 75 screw-fitted into the force-transmitting lever 21. This adjusting screw 75 is, for instance, secured in its setting by means of a securing fluid. The additional no-load spring 73 is provided with an angular bend 76 at one end which, after the no-load control spring 28 has travelled through path b, engages with the latter spring and assists the action of the latter on the adaptor sleeve 15. Apart from the additional no-load spring 73, there is also a bi-metal spring 77 secured to the forcetransmitting lever 21, which spring 77 changes its position, in case of a cold engine, in such a way as to additionally act upon the regulator member 15 by way of the first control spring 28, which action results in an increased idling speed, as is required for the smooth running of a cold engine. Both additionallly provided springs 73 and 77 may, ofcourse, be omitted in the case of simple regulating conditions.

The governor housing 37 is closed by means of a cover 78 on the frontal face thereof away from the injection pump, which cover allows, after its removal, access to all essentially horizontally disposed adjusting elements of the governor. These adjusting elements are, to summarize them, the bearing bolt 49 for adjusting the proportional range of the governor, the stop screw 41 for the adjustment of the non-operational position of the force-transmitting lever 21, the adjusting screw 47 for changing the bias of the control spring 42, the adjusting screw 34 for changing the bias of the noload control spring 73, and the adjusting element 23 for the adjustment of the first partial travel a of the path of the adaptor sleeve 15, which travel a is normally identical with the idling stroke of the adaptor sleeve 15.

The governor operates as follows:

All movable parts of the governor have been illustrated in non-operating position; the operating lever 68 and therewith the steering lever 66 are in their rest position. For starting the internal combustion engine, the operating lever 68 and therewith the steering lever 66 (see FIG. 3 for this detail) are brought into full-load position by swivelling in the direction of the arrow 79, which results in shifting of the control rod 56 by means of the cam lever 54 and by way of the accumulator 55 in the direction of the arrow 80 into the starting position. In the starting position of the control rod 56, the injection pump delivers a quantity of fuel to the internal combustion engine, which is in excess of the fuel quantity required for full load operation in order to facilitate the starting of the engine.

After the engine has been started, and while the operating lever 68 is, for instance, being kept in the full load position, the rpm rises further and the centrifugal fly weights l2 swing outwardly, under the influence of the centrifugal forces, from their position as shown in the drawing. The centrifugal fly weights 12 thereby transmit the adjusting forces with their arms 13 via the thrust collar 14 and the thrust bearing 16 to the adaptor sleeve 15, which is displaced against the force of the no-load control spring 28 until it abuts with its front face 27 at the end plane 26 of the adjusting element 23, which is screw-fitted into the force-transmitting lever 21. This displacement of the adaptor sleeve 15 by the partial travel path a causes the bearing arm 61 with the ball joint 57 to be displaced by the same length of travel, and the control rod 56 is shifted by means of the linkage members 53, 54 and 55 from the starting position into the full load position. The governor remains in this position as the rpm increases further until the final rpm is reached, which is predetermined by the bias of the second control spring 42 serving as main control spring. If this final rpm is exceeded in the case of the engine operating under partial load, the force transmitting lever 21 lifts off its stop 39 due to the increasing force at the adaptor sleeve 15, and the latter travels further beyond the partial distance a. The adaptor sleeve 15 thereby moves the linkage members 53, 54, 55 and the control rod 56 into a position in which the fuel quantity of the injection pump is decreased until it corresponds with the power output of the motor and until the rpm is maintained within the proportional range. As the forces of the control spring 42 are taken up, on the one hand, by the abutment 44, and, on the other hand, by the stop 39 of the force transmitting lever 21 or by the adaptor sleeve 15, the linkage members 53, 54 and 55 are free from resetting forces in all operating conditions. If, for example, the control rod 56 abuts in its end position against a stop not shown in the drawing, and if the operating lever 68 of the governor moves beyond a setting corresponding with the said stop, a spring of the accumulator 55 is compressed, and only these relatively small forces are transmitted to the linkage members.

Due to the fact that, as mentioned above, all adjusting elements are acessible from the one front end of the governor, and since they are all arranged in parallel or at least approximately in parallel with one another, the centrifugal rpm-regulating governor according to this invention is particularly suited for an automated setting. But even without such automated setting, the centrifugal governor according to the invention offers the advantage that all adjusting elements are accessible from one end only, and that they can be adjusted independently of each other, i.e., without influencing the function of other adjusting elements.

A further advantage resides in the fact that the noload control spring 28, the additional no-load spring 73, as well as the bi-rnetal spring 77 with their associated adjusting screws 34 and 75 are supported at the force-transmitting lever 21, whereby these springs are fixedly clamped, upon abutment of the front face 27 of the adaptor sleeve at the supporting lever 21, or at its adjusting element 23, so that they no longer have any influence on the regulation of the final rpm. A further advantage to be noted is that the spacings of the adjusting elements 23, 34, 41, 47, 49 and 75 do not change during the various adjusting procedures, but remain constant, which fact facilitates a rapid and optionally an automated setting of the governor, as, for this purpose, a multiple-adjusting tool having adjusting means arranged in parallel can be applied from the front end of the regulator.

What is claimed is:

1. In a centrifugal governor for controlling the rpm of an injection type internal combustion engine having a fuel injection pump, which governor has a housing and a regulator member being displaceable as a function of the rpm, and the regulating movements of which member are transmitted, by means of a two-armed cam lever having lever arms which are adjustable dependent upon the position given an externally turnable operating lever, to fuel delivery control means associated with said fuel injection pump, wherein said fuel delivery control means, upon completing a first part of its movement against the force of a first control spring, acts on a force-transmitting lever which is biassed by at least one second control spring, and said force-transmitting lever bears an adjusting screw for setting said first control spring to a low rpm, and is adapted for swivelling about an axis which is stationary in said housing, and wherein the neutral position of said force-transmitting lever is determined by a stop fixed in said housing, the improvement comprising a. a bearing lever adjustable for setting a maximum rpm and bearing a spring seat for said second control spring,

b. a second adjusting screw for said bearing lever,

and

c. an adjusting element for limiting the first part of the movement of said regulator member,

said bearing lever, second adjusting screw and adjusting element being in engagement with said forcetransmitting lever.

2. The improvement as described in claim 1, wherein said force-transmitting lever is arranged, in its neutral position, at least approximately perpendicular to the axis of said regulator member.

3. The improvement as described in claim 1, wherein said regulator member is an adaptor sleeve.

4. The improvement as described in claim 1, wherein said bearing lever is an angle lever having a pivot axis stationary relative to said force-transmitting lever.

5. The improvement as described in claim 1, wherein said adjusting screw for setting said first control spring, said adjusting element and said second adjusting screw for said bearing lever are disposed in parallel with one another and at least approximately in parallel with the axis of said regulator member, and are screwconnected to said force-transmitting lever and secured in their position thereon.

6. The improvement as described in claim 1, further comprising a stop screw screwed into said governor housing in a position at least approximately in parallel with said adjustment screws and with said adjusting element, said stop screw forming an abutment for said force-transmitting lever.

7. The improvement as described in claim 1, wherein said second control spring is a tension spring which is disposed at least approximately in parallel with said force-transmitting lever.

8. The improvement as described in claim 7, further comprising a bearing bolt mounted in said governor housing in parallel with the axis of said regulator member and being turnable for changing the active direction of said tension spring and thereby adjusting the proportional range of the governor.

9. The improvement as described in claim 8, wherein said tension spring engages at its one end said bearing bolt, and at its other end said bearing lever.

10. The improvement as described in claim 9, wherein said bearing bolt is provided with a helicoidal groove in which said one end of said tension spring is held.

11. The improvement as described in claim 1, wherein said force-transmitting lever is of U- or l-l-type cross sectional configuration and has two parallel legs facing toward said injection pump.

12. The improvement as described in claim 11, further comprising a pivot pin mounted traversely in said legs of said force-transmitting lever and serving as pivot for said bearing lever.

13. The improvement as described in claim 11, wherein each of said legs is provided with a guiding slot, and said regulator member is provided with a pair of guide-pins being inserted each in one of said guiding slots.

14. The improvement as described in claim 13,

. wherein said first control spring is a leaf spring, wherein 15. The improvement as described in claim 14, wherein said adjusting screw for said first control spring is screw-connected to and secured in position at said force-transmitting lever in the cross part thereof intermediate said two legs and engages said leaf spring intermediate the ends thereof.

16. the improvement as described in claim 1, further comprising an additional no-load control spring supported on said force-transmitting lever and adapted for engagement by said first control spring so as to increase the bias of the latter, and a third adjusting screw screwed into said force-transmitting lever and adapted for changing the effective range of engagement of said additional no-load spring with said first control spring, said latter spring being adapted for affecting the operafirst control spring on said regulator member. 

1. In a centrifugal governor for controlling the rpm of an injection type internal combustion engine having a fuel injection pump, which governor has a housing and a regulator member being displaceable as a function of the rpm, and the regulating movements of which member are transmitted, by means of a twoarmed cam lever having lever arms which are adjustable dependent upon the position given an externally turnable operating lever, to fuel delivery control means associated with said fuel injection pump, wherein said fuel delivery control means, upon completing a first part of its movement against the force of a first control spring, acts on a force-transmitting lever which is biassed by at least one second control spring, and said forcetransmitting lever bears an adjusting screw for setting said first control spring to a low rpm, and is adapted for swivelling about an axis which is stationary in said housing, and wherein the neutral position of said force-transmitting lever is determined by a stop fixed in said housing, the improvement comprising a. a bearing lever adjustable for setting a maximum rpm and bearing a spring seat for said second control spring, b. a second adjusting screw for said bearing lever, and c. an adjusting element for limiting the first part of the movement of said regulator member, said bearing lever, second adjusting screw and adjusting element being in engagement with said force-transmitting lever.
 2. The improvement as described in claim 1, wherein said force-transmitting lever is arranged, in its neutral position, at least approximately perpendicular to the axis of said regulator member.
 3. The improvement as described in claim 1, wherein said regulator member is an adaptor sleeve.
 4. The improvement as described in claim 1, wherein said bearing lever is an angle lever having a pivot axis stationary relative to said force-transmitting lever.
 5. The improvement as described in claim 1, wherein said adjusting screw for setting said first control spring, said adjusting element and said second adjusting screw for said bearing lever are disposed in parallel with one another and at least approximately in parallel with the axis of said regulator member, and are screw-connected to said force-transmitting lever and secured in their position thereon.
 6. The improvement as described in claim 1, further comprising a stop screw screwed into said governor housing in a position at least approximately in parallel with said adjustment screws and with said adjusting element, said stop screw forming an abutment for said force-transmitting lever.
 7. The improvement as described in claim 1, wherein said second control spring is a tension spring which is disposed at least approximately in parallel with said force-transmitting lever.
 8. The improvement as described in Claim 7, further comprising a bearing bolt mounted in said governor housing in parallel with the axis of said regulator member and being turnable for changing the active direction of said tension spring and thereby adjusting the proportional range of the governor.
 9. The improvement as described in claim 8, wherein said tension spring engages at its one end said bearing bolt, and at its other end said bearing lever.
 10. The improvement as described in claim 9, wherein said bearing bolt is provided with a helicoidal groove in which said one end of said tension spring is held.
 11. The improvement as described in claim 1, wherein said force-transmitting lever is of U- or H-type cross sectional configuration and has two parallel legs facing toward said injection pump.
 12. The improvement as described in claim 11, further comprising a pivot pin mounted traversely in said legs of said force-transmitting lever and serving as pivot for said bearing lever.
 13. The improvement as described in claim 11, wherein each of said legs is provided with a guiding slot, and said regulator member is provided with a pair of guide-pins being inserted each in one of said guiding slots.
 14. The improvement as described in claim 13, wherein said first control spring is a leaf spring, wherein a fixed spring seat for one end of said leaf spring is located on said force-transmitting lever between the two legs thereof, and wherein the other end of said leaf spring abuts said guide pins of said regulator member.
 15. The improvement as described in claim 14, wherein said adjusting screw for said first control spring is screw-connected to and secured in position at said force-transmitting lever in the cross part thereof intermediate said two legs and engages said leaf spring intermediate the ends thereof.
 16. the improvement as described in claim 1, further comprising an additional no-load control spring supported on said force-transmitting lever and adapted for engagement by said first control spring so as to increase the bias of the latter, and a third adjusting screw screwed into said force-transmitting lever and adapted for changing the effective range of engagement of said additional no-load spring with said first control spring, said latter spring being adapted for affecting the operation of said regulator member during at least a part of the travel of said regulator member from rest position into contact with said adjusting element.
 17. The improvement as described in claim 16, wherein said first control spring and said additional no-load control spring are both leaf springs.
 18. The improvement as described in claim 16, further comprising a bi-metal spring supported on said force-transmitting lever and adapted for acting via said first control spring on said regulator member. 